Noise and vibration management for smoke evacuation system

ABSTRACT

A system for noise and vibration management of a smoke evacuation system includes a pump that compresses air and produces a pressure differential within an airflow path. The pump may be a sealed, positive displacement pump. The system includes vibration absorption mechanisms disposed between inner and outer housings, as well as on the outside surface of the outer housing. Methods of controlling and regulating a motor of the system to preserve the lifespan of the motor and maintain consistent airflow rates throughout the smoke evacuation system include varying a supply of electrical current to the motor so that it can operate at variable performance levels. Orifices are opened and closed in order to relieve resistance pressures within the airflow path due to clogging and blockages.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of U.S. patent application Ser. No.15/826,370, filed Nov. 29, 2017, and entitled Noise and VibrationManagement For Smoke Evacuation System, the entire content of which isincorporated herein by reference.

BACKGROUND 1. Technical Field

The present disclosure relates to smoke evacuation systems used inelectrosurgical systems. More specifically, the present disclosurerelates to apparatus and methods of dampening vibrations and noisecaused by a smoke evacuation system.

2. The Relevant Technology

As is known to those skilled in the art, modern surgical techniquestypically employ radio frequency (RF) power to cut tissue and coagulatebleeding encountered in performing surgical procedures. Suchelectrosurgery is widely used and offers many advantages including theuse of a single surgical instrument for both cutting and coagulation. Amonopolar electrosurgical generator system has an active electrode, suchas in the form of an electrosurgical instrument having a hand piece anda conductive electrode or tip, which is applied by the surgeon to thepatient at the surgical site to perform surgery and a return electrodeto connect the patient back to the generator.

The electrode or tip of the electrosurgical instrument is small at thepoint of contact with the patient to produce an RF current with a highcurrent density in order to produce a surgical effect of cutting orcoagulating tissue through cauterization. The return electrode carriesthe same RF signal provided to the electrode or tip of theelectrosurgical instrument, after it passes through the patient, thusproviding a path back to the electrosurgical generator.

Electrosurgical instruments communicate electrical energy to a targettissue of a patient to cut the tissue and/or cauterize blood vesselswithin and/or near the target tissue. This cutting and cauterizationresult in smoke released into the air that can be unpleasant andobstructive of the view of a practitioner. Many electrosurgical systemsmay therefore employ a smoke evacuation system that captures theresulting smoke and directs it through a filter and exhaust port, awayfrom practitioners and/or patients.

Smoke evacuation systems typically comprise a fan and a filter. The fancreates suction that draws smoke through a vacuum tube into the filter.A vacuum tube may terminate at the hand piece that includes theelectrode tip so that the smoke is sucked in at the hand piece. Otherelectrosurgical systems may include separate hand pieces that are usedto suck the smoke into the system. The smoke travels to the filter via avacuum tube and offensive smells are filtered out as the smoke movesthrough the filter. Filtered air may then exit the smoke evacuationsystem as exhaust.

The subject matter claimed herein is not limited to embodiments thatsolve any disadvantages or that operate only in environments such asthose described above. Rather, this background is only provided toillustrate one exemplary technology area where some embodimentsdescribed herein may be practiced.

BRIEF SUMMARY

The present disclosure relates to smoke evacuation systems. Morespecifically, the present disclosure relates to methods and apparatusesfor managing noise and vibrations of smoke evacuation systems. Noise andvibrations produced by smoke evacuation systems can be distracting andirritating to practitioners performing surgery. The present disclosurerelates to methods and apparatuses for reducing noise and vibrationsassociated with smoke evacuation systems.

In one embodiment, a smoke evacuation system includes a filter, a pumpthat has a sealed positive displacement airflow path, and a motor thatdrives the pump. The sealed positive displacement airflow path of thepump may comprise one or more circulation paths of a gas within thepump. In one embodiment, the pump has a first operating pressure and asecond operating pressure. The flow rate of a gas being pumped may bethe same regardless of the operating pressure. The pump may compressincoming gas to create a pressure difference between various zones ofairflow within the smoke evacuation system.

In one embodiment, a smoke evacuation system may include variousvibration absorption mechanisms. The system may have a first housingenclosing the motor and the pump and a second housing enclosing theentire system. Vibration mechanisms may be disposed between the twohousings and outside the second housing. Flexible tubing may also beincorporated to absorb vibrations.

A method of reducing the vibrations and noise of a smoke evacuationsystem may include regulating the motor engaged with the pump. Theregulation of the motor may include varying a supply of current to themotor in order to operate the motor in at least two distinct operatinglevels. Regulation of the motor may depend on sensory inputs, such astemperature or pressure. Orifices may also be provided within theairflow path that allow communication with ambient surroundings of thesystem in order to relieve excessive resistance pressures in the systemcaused by blockages or clogging of the airflow path.

This Summary is provided to introduce a selection of concepts in asimplified form that are further described below in the DetailedDescription. This Summary is not intended to identify key features oressential features of the claimed subject matter, nor is it intended tobe used as an aid in determining the scope of the claimed subjectmatter.

Additional features and advantages of the disclosed embodiments will beset forth in the description which follows, and in part will be obviousfrom the description, or may be learned by the practice of thedisclosure. These and other features will become more fully apparentfrom the following description and appended claims, or may be learned bythe practice of the present disclosure.

BRIEF DESCRIPTION OF THE DRAWINGS

To further clarify the above and other advantages and features of thepresent invention, a more particular description of the invention willbe rendered by reference to specific embodiments thereof which areillustrated in the appended drawings. It is appreciated that thesedrawings depict only illustrated embodiments of the invention and aretherefore not to be considered limiting of its scope. The invention willbe described and explained with additional specificity and detailthrough the use of the accompanying drawings in which:

FIG. 1 illustrates an embodiment of an electrosurgical system;

FIG. 2 illustrates a schematic of an embodiment of a smoke evacuationsystem;

FIG. 3 illustrates resistance pressure vs. air flow for a sealedpositive displacement pump and a fan;

FIG. 4 illustrates a table comparing various specifications of a fan,blower, and compressor.

FIG. 5A illustrates an exploded view of a hybrid regenerative blower;

FIG. 5B illustrates a cross-sectional view of the hybrid regenerativeblower illustrated in FIG. 5A;

FIGS. 6A through 6C illustrate cross-sectional views of various stagesof a claw pump;

FIG. 7A illustrates one embodiment of a lobe compressor having twolobes;

FIG. 7B illustrates one embodiment of a lobe compressor having threelobes;

FIG. 7C illustrates one embodiment of a lobe compressor having fivelobes;

FIG. 8 illustrates a cross-sectional view of on embodiment of a scrollcompressor;

FIG. 9 illustrates one embodiment of a dual, in-line scroll compressor;

FIG. 10A illustrates one embodiment of a high flow and a low flowscroll;

FIG. 10B illustrates the relationship of time vs. airflow for both thelow flow scroll and the high flow scroll illustrated in FIG. 10A;

FIG. 11 illustrates an embodiment of a smoke evacuation system includinginner and outer housings;

FIG. 12 illustrates on embodiment of vibration absorption mechanismsdisposed between inner and outer housings;

FIG. 13A illustrates one embodiment of vibration absorption mechanismsdisposed between inner and outer housings;

FIGS. 13B and 13C illustrate various cross-sectional views of thevibration absorption mechanisms illustrated in FIG. 13A;

FIG. 14A illustrates one embodiment of a vibration absorption mechanism;

FIG. 14B illustrates a cross-sectional view of the vibration absorptionmechanism illustrated in FIG. 14A;

FIG. 15 illustrates one embodiment of a vibration absorption mechanism;

FIGS. 16A through 16C illustrate various embodiments of vibrationabsorption mechanisms;

FIG. 17A illustrates one embodiment of a vibration absorption mechanism;

FIG. 17B illustrates a cross-sectional view of one of the vibrationabsorption mechanisms illustrated in FIG. 17A;

FIG. 17C illustrates one embodiment of a vibration absorption mechanism;

FIG. 18A illustrates one embodiment of a vibration absorption mechanism;

FIG. 18B illustrates a cross-sectional view of the vibration absorptionmechanisms illustrated in FIG. 18A;

FIG. 19A illustrates a cross-sectional view of one embodiment of avibration absorption mechanism;

FIG. 19B illustrates the vibration absorption mechanism illustrated inFIG. 19A, but undergoing deformation due to vibrations; and

FIG. 20 illustrates a flowchart showing a method of reducing noise andvibration of a smoke evacuation system.

DETAILED DESCRIPTION Introduction

The present disclosure relates to smoke evacuation systems. Morespecifically, the present disclosure relates to methods and apparatusesfor managing noise and vibrations of smoke evacuation systems. Noise andvibrations produced by smoke evacuation systems can be distracting andirritating to practitioners performing surgery. The present disclosurerelates to methods and apparatuses for reducing noise and vibrationsassociated with smoke evacuation systems.

FIG. 1 illustrates an exemplary electrosurgical system 100. Theillustrated embodiment includes a signal generator 102, anelectrosurgical instrument 104, a return electrode 106, and a smokeevacuation system 120. Generator 102, in one embodiment, is an RF wavegenerator that produces RF electrical energy. Connected toelectrosurgical instrument 104 is a utility conduit 108. In theillustrated embodiment, utility conduit 108 includes a cable 110 thatcommunicates electrical energy from generator 102 to electrosurgicalinstrument 104. The illustrated utility conduit 108 also includes avacuum hose 112 that conveys captured/collected smoke and/or fluid awayfrom a surgical site.

Generally, electrosurgical instrument 104 includes a hand piece orpencil 114 and an electrode tip 116. Electrosurgical instrument 104communicates electrical energy to a target tissue of a patient to cutthe tissue and/or cauterize blood vessels within and/or near the targettissue. Specifically, an electrical discharge is delivered fromelectrode tip 116 to the patient in order to cause heating of cellularmatter of the patient that is in close contact with or adjacent toelectrode tip 116. The tissue heating takes place at an appropriatelyhigh temperature to allow electrosurgical instrument 104 to be used toperform electrosurgery. Return electrode 106 is connected to generator102 by a cable 118, and is either applied to or placed in closeproximity to the patient (depending on the type of return electrodeused), in order to complete the circuit and provide a return electricalpath to wave generator 102 for energy that passes into the patient'sbody.

The heating of cellular matter of the patient by the electrode tip 116,or cauterization of blood vessels to prevent bleeding, results in smokebeing released from the heated tissue. The electrosurgical instrument104 may comprise a smoke evacuation conduit opening 122 near theelectrode tip 116 so as to be able to capture the smoke that is releasedduring a procedure. Vacuum suction may draw the smoke into the conduitopening 122, through the electrosurgical instrument 104, and into thevacuum hose 112 toward the smoke evacuation system 120.

FIG. 2 illustrates a schematic of an embodiment of a smoke evacuationsystem 400. The smoke evacuation system 400 may include a filter 406 andan airflow path 408. The airflow path 408 may comprise a pump 410disposed in-line with the airflow path 408 producing a pressuredifference within the airflow path 408 by mechanical action. Thispressure difference may cause movement of a gas through the airflow path408.

The airflow path 408 may be at least partially comprised of a tube orother conduit that substantially contains and/or isolates the air movingthrough the airflow path 408 from air outside the airflow path. Forexample, the first zone 416 of the airflow path 408 may comprise a tubethrough which the airflow path 408 extends between the filter 406 andthe pump 410. The second zone 418 of the airflow path 408 may alsocomprise a tube through which the airflow path 408 extends between thepump 410 and the exhaust mechanism 414. The airflow path 408 alsoextends through the filter 406, pump 410, and exhaust mechanism 414 sothat a continuous airflow path 408 extends through the smoke evacuationsystem 400.

The gas drawn through the airflow path 408 may be smoke 402, or thefiltered air remaining after the smoke 402 has passed through the filter406. A motor 412 drives the pump 410. The smoke evacuation system 400may also include an exhaust mechanism 414 that may also be disposedin-line with the airflow path 408. The airflow path 408 may extend fromthe inlet port 245 to the outlet port 250 and pass through the filter406, pump 410 and exhaust mechanism 414

Pumps

The pump 410 may cause a suction of smoke 402 that has travelled throughthe vacuum tube 112 illustrated in FIG. 1 to the filter illustrated inFIG. 2 . The smoke 402 may be drawn to the filter 406 via a suctioncreated by the pump 410 as discussed above. The pump 410 may create apressure difference between a first zone 416 and a second zone 418 ofthe airflow path 408. This pressure difference causes the smoke 402 totravel into the filter 406, which is disposed at an inlet of the airflowpath 408, through the airflow path 408, and out the exhaust mechanism414, which is disposed at an outlet of the airflow path 408. The filter406 may extract potentially harmful, foul, or otherwise unwantedparticulates from the smoke 402.

The pump 410 may be disposed in-line with the airflow path 408, meaningthe gas flowing through the system enters the pump 410 at one end andexits the pump 410 at the other end. The pump 410 may provide a sealedpositive displacement airflow path. The pump 410 may produce the sealedpositive displacement airflow path by trapping (sealing) a first volumeof gas and decreasing that volume to a second smaller volume as the gasmoves through the pump 410. Decreasing the volume of the trapped gasincreases the pressure of the gas. The second pressurized volume of gasmay then be released from the pump at a pump outlet. The pump releasesthe pressurized outlet gas into the airflow path 408 and on towards theexhaust mechanism 414. More details regarding various embodiments ofpumps that may provide a sealed positive displacement airflow path aredescribed herein.

The pump 410 may have more than one operating pressure. The pump 410 mayoperate at various operating pressures while maintaining a similar flowrate through the airflow path 408. For example, the pump 410 may operateat a first operating pressure resulting in a first flow rate of gasthrough the airflow path 408. The pump 410 may also operate at a secondoperating pressure resulting in a second flow rate. The first and secondflow rates of gas through the airflow path 408 may be the same orsubstantially similar regardless of the difference in the first andsecond operating pressures of the pump 410. For example, if blockage orclogging occurs in the airflow path 408, causing a higher pressurewithin the path 408, the pump 410 may operate at that higher pressurewhile still maintaining a constant flow rate of air/gas through theairflow path 408.

The terms “pump” and “sealed positive displacement pump” as used hereinmay refer to mechanisms that may transfer or cause movement of a gas bymechanical action and substantially increase the pressure of that gas asthe gas is moved. For instance, as used herein, a pump may refer to anynumber of different blowers or compressors. Fans, on the other hand, arenot considered “pumps” for purposes of this disclosure. Fans may onlyoperate at a pressure ratio of about 1:1. This pressure ratio does notprovide a substantial increase in pressure of the gas being moved.

Fans and pumps differ in many respects. A fan may include rotatingblades that create a current or flow of gas from one side of the fan tothe other. Fans typically operate at a pressure ratio of about 1:1 andmove a relatively high volume of air. Typical fans used in smokeevacuation systems may have an operational pressure between atmosphericpressure to about 1.5 psig. The volumetric airflow capacity of a fandecreases dramatically when blockages increase a pressure resistanceinside the airflow path 408, as shown in FIG. 3 . A sealed positivedisplacement pump, as described above, is affected less by suchblockages and performs well against high resistance pressures, as seenin FIG. 3 .

Fans may create suction that draws air through the smoke evacuationsystem, but they are typically very noisy. The noise can be distractingto practitioners performing surgery. Fans used in typical systems cancreate sufficient suction but struggle to maintain consistent suctionwhen resistance pressures increase in the system due to airflowobstructions or clogging. Fans are prone to create weak and inconsistentairflow rates through the system.

Blowers differ from fans in that they operate at a higher pressure ratio(e.g., between about 1:1 to 1:2). Essentially, a blower is a high-speedand/or high-volume fan. For example, a blower may be a centrifugal fanthat uses rotating impellers to increase the speed and volume of a gaspassing through it. Blowers typically have an operational pressurebetween 1.5 and 1.72 psig and transfer a very high volume of gasrelative to fans and compressors.

Compressors are pumps that move relatively low volumes of gas with muchhigher pressure ratios than fans and blowers. A typical pressure ratiofor a compressor, such as those described in various embodiments herein,may be greater than about 2:1. Compressors may operate at a pressure ofgreater than about 2.72 psig. The various compressors described herein,particularly embodiments that include positive displacement compressors,may be advantageous for a number of reasons. Positive displacement pumpsmay be much quieter than typical fans used in smoke evacuation systems.Positive displacement pumps also operate well against resistancepressures due to blockages in the airflow path 408 of the smokeevacuation system 400.

Blockages may include unwanted particulate build-up or other cloggingdue to objects from the ambient air being sucked into the airflow path408. FIG. 3 illustrates the relationship between pressure resistance andairflow for a positive displacement pump vs. a typical fan. As shown, asealed positive displacement pump may maintain a relatively steadyairflow regardless of the pressure resistance in the system due toclogging. In contrast, the airflow capability of a fan decreasesdramatically as the pressure resistance rises. In practice, thisindicates that sealed positive displacement pumps, such as the variousembodiments described herein, may still create a suction through thesmoke evacuation system 400 even when the system clogs or becomesblocked. This is typically not the case if a fan is used.

FIG. 4 is a table showing the pressure increase, operational pressure,pressure ratio, and air volume transferred by a fan, blower, andcompressor for comparison. As shown, compressors are able to produce apressure ratio of greater than 2:1 between a low-pressure gas enteringthe pump 410 from a first zone 416 of the airflow path 408 and apressurized gas exiting the pump 410 into a second zone 418 of theairflow path 408.

FIG. 4 also shows the relative air volume moved by the fans, blowers,and compressors. Compressors move the lowest volume of air relative tofans and blowers, and fans move the highest volume of air when air flowpath conditions are equivalent. FIG. 4 also shows that compressorsoperate at a pressure ratio of greater than 2:1, as opposed to fans andblowers that operate at pressure ratios closer to 1:1. This means thatair/gas exiting a compressor is typically pressurized at twice thepressure of the air/gas entering the compressor at a compressor inlet.

The various embodiments of the smoke evacuation system, as describedherein, may include one or more various types of pumps. The variouspumps may be incorporated into the system in order to reduce noise andvibrations, which can be irritating to users and damaging to the system.For example, typical fans used in current systems may be very noisy andcause significant vibrations. These vibrations can cause the system totravel along a surface where it is placed, thus requiring a secureconnection to that surface. This secure connection diminishes theportability of the system and increases the difficulty of installation.Vibrations can also be damaging to internal components of the system,which may not be designed to withstand such vibrations.

The following description includes various embodiments of a smokeevacuation system, including various types of pumps, vibrationabsorption mechanisms, and motor control methods aimed at reducing thenoise and vibration of the system in order to solve these problems.

In one embodiment of a smoke evacuation system 400, the pump 410 shownin FIG. 2 may be a blower 420, as illustrated in FIGS. 5A-5B. FIG. 5Aillustrates an exploded view of blower 420. The blower 420 may be ahybrid regenerative blower with impeller features that compress the gas402 passing there through. The blower 420 may include a top cover 422, abottom cover 424, and an impeller assembly 426. A rotary shaft 428 maybe secured to the center of the impeller assembly 426 and cause theimpeller assembly 426 to rotate. A motor 412 that may engage the rotaryshaft 428 is not illustrated in FIG. 5A, but is shown in FIG. 2 .

The top cover 422 may be secured to the bottom cover 424 to create asealed circulation path 430 having an inlet 432 and an outlet 434. Thecirculation path 430 may also be referred to as an airflow path 430 ofthe blower. The impeller assembly 426 may be disposed between the topcover 422 and bottom cover 424 so that the impeller blades 436 residewithin the sealed circulation path 430. A motor drives the impellerassembly 426 to rotate about the rotary shaft 428 so that the impellerblades 436 travel in a circular path through the sealed circulation path430. This circular motion of the impeller blades 436 creates a suctionso that a gas 402 is drawn into the inlet 432, travels around the sealedcirculation path 430, and exits the blower 420 out of the outlet 434.

FIG. 5B illustrates the flow path 438 of a gas 402 flowing through thesealed circulation path 430 of the blower 420. FIG. 5B illustrates across-sectional view of the blower 420 showing impeller assembly 426inside sealed circulation path 430. The impeller assembly 426 is drivenclockwise in this embodiment. As the impeller blades 436 rotate throughthe sealed circulation path 430, centrifugal force moves gas moleculesfrom the blade root 440 to its tip 442. The gas molecules then leave theblade tip 442 and enter the portion of the sealed circulation path 430not occupied by the impeller blades 436. The gas molecules are thendrawn back down a succeeding impeller blade 436 in repeated fashion.

This repeated flow path 438 of the gas provides a quasi-staging effectthat may increase a pressure differential capability of the blower 420.This type of regenerative blower 420 passes the gas through manycompression cycles as the gas molecules pass up and down variousimpeller blades 436 with each revolution of the impeller assembly 426.Thus, a gas exiting the outlet 434 may have a higher pressure than thegas entering at the inlet 432. The speed of the rotating impellerassembly 426 is proportional to the pressure differential of the gas.For example, a higher rotational speed of the impeller assembly 426increases the pressure differential between the gas at the inlet 432compared to the gas exiting at the outlet 434. A lower rotational speedresults in a lower pressure differential.

The number of impeller blades 436 may be odd so as to limit resonance,which can create noise and vibrations. An odd number of blades 436reduces the chance of elastic frequencies from the blades 436 becomingtuned to a resonant frequency of the rotary shaft 428. Naturalfrequencies of the top and bottom covers 422, 424 are also offset fromthe frequencies of the blades 436 and rotary shaft 428 to limit noiseand vibrations of the blower 420 due to the harmonics of the blower 420.

In one embodiment of a smoke evacuation system 400, the pump 410 shownin FIG. 2 may be a claw pump 444. Various cross-sectional views of theclaw pump 444 are illustrated in FIGS. 6A-6C. The claw pump 444 may be acooperative dual drive shaft claw pump. FIGS. 6A-6C illustrate a topcross-sectional view of the claw pump 444 in three different stages ofrotation. The claw pump 444 is a positive displacement pump thatcompresses gas by decreasing the volume of an initial volume of gas thatenters the pump.

The claw pump 444 may have first and second counter-rotating rotaryelements, or claws 446, 448 disposed within a single circulation path ofthe pump 444. For example, the first claw 446 may rotate clockwise andthe second claw 448 may rotate counter-clockwise, as indicated by thearrows in FIG. 6B. FIG. 6A shows an initial state of the claw pump 444where a gas 450 resides in a sealed space between the claws 446, 448 andthe pump housing 452. The gas 450 is illustrated in gray. As the claws446, 448 rotate, the volume of the sealed space in which the gas 450resides decreases due to the geometry of the claws 446, 448. FIG. 6Cillustrates the gas 450 in a compressed state, where the volume of thesealed space in which the gas 450 resides has been reduced due to therotation of the claws 446, 448.

Decreasing the volume of the gas 450 pressurizes the gas. The inlet andoutlet ports of the claw pump 444 are not shown in detail because of thetop cross-sectional view of FIGS. 6A-6C. An inlet 456 may, for example,be disposed below the claw pump 450 an outlet 454 may be disposed abovethe claw pump 444 so that the compressed volume of gas 450 shown in FIG.6C may enter and exit via the inlet 456 and outlet 454 perpendicular tothe viewing plane. In other words, the inlet 456 and outlet 454 may beconfigured so that the inlet 456 is disposed below the viewing plane andthe outlet 454 is disposed above the viewing plane, or vice versa, sothat the gas travels through the claw pump 444 perpendicular to theviewing plane.

Embodiments of the smoke evacuation system 400 that may include acooperative dual drive shaft claw pump 444 such as the one illustratedin FIGS. 6A-C may enjoy reduced noise and vibrations. Pumps with singleshaft rotary elements may suffer from vibrations due to slightimbalances of components that rotate around a central drive shaft. Inthe cooperative dual drive shaft claw pump 444 illustrated, the tworotating claws 446, 448 rotate in opposite directions and may balanceeach other out. This balance may minimize vibrations.

In one embodiment, the pump 410 of the smoke evacuation system 400 mayalso be a lobe compressor 458. FIG. 7A illustrates a cross-sectionalview of a lobe compressor 458 including two counter-rotating rotaryelements 460, 462. Each rotary element 460, 462 may have two or morelobes 478. The lobe compressor 700 functions similarly to the claw pump444 described herein, in that the two rotary elements 460, 462 rotate inopposite directions, as indicated by the arrows marked on the two rotaryshafts 470, 472, in order to create a sealed positive displacementairflow path through the compressor 458.

The rotation of the rotary elements 460, 462 draws in a low-pressure gas474 through an inlet 466 and moves the gas 474 through the compressor458 to an outlet 468. As the gas 474 moves through the compressor 458,as indicated by the arrows, the volume of the gas 474 decreases, whichpressurizes the gas. The pressurized gas 476 then exits the compressor458 via the outlet 468.

Other embodiments of the smoke evacuation system 400 may include lobecompressors 700 having more than two lobes 478 on each rotary element460, 462. For example, FIG. 7B illustrates a lobe compressor 480 thatcomprises two rotary elements 460, 462 having three lobes 478 each. Inthis embodiment, a low-pressure gas is drawn into the inlet 466, driventhrough the compressor 480 via the rotating lobes 478, after which thevolume of the inlet gas is reduced and pressurized before it exits outthe outlet 468 of the compressor 480.

FIG. 7C illustrates yet another embodiment of a lobe compressor 482 thatoperates similar to the other lobe compressors described herein. Thelobe compressor 482 illustrated in FIG. 7C includes two rotary elements460, 462 that have five lobes each. Other embodiments may include lobecompressors with rotary elements that have four lobes, or more than fivelobes.

In the various embodiments of lobe compressors illustrated in FIGS.7A-7C, the two rotary elements maintain consistent contact with eachother while rotating. For instance, each lobe 478 of one rotary elementextends between two lobes of the other rotary element so that contact ismaintained as the rotary elements rotate. Thus, air may not escape frombetween the lobes. Instead, the air is trapped within sealedcompartments as the air moves through the lobe compressors.

Other embodiments of a smoke evacuation system 400 may include multiplerotary elements that cooperatively counter-rotate to produce a sealedcirculation path that traps and compresses gas by positive displacementaction. These other pumps may include, but are not limited to, two stagerotary vane pumps and dual screw eccentric pumps. The various counterrotating dual drive shaft pumps with multiple rotary elements describedherein may provide a pressure differential of at least 1.5 psig betweena low-pressure inlet gas entering the pump 410 from a first zone 416 ofthe airflow path 408 and a high-pressure outlet gas exiting the pump 410into a second zone 418 of the airflow path 408. Other embodiments mayinclude similar pumps that produce a pressure differential of between 1and 2 psig. Yet other embodiments may produce a pressure differential ofgreater than 2 psig.

The various counter rotating dual drive shaft pumps with multiple rotaryelements may also reduce vibration and noise within the smoke evacuationsystem 400 for the same reasons as discussed above in reference to theclaw pump 444. The two rotary elements rotate in opposite directions andbalance each other out. This balance may cancel out vibrations andresulting noise.

In one embodiment of the smoke evacuation system 400, the pump 410 maybe a scroll compressor. Scroll compressors are positive displacementcompressors. The various embodiments of a scroll compressor describedherein may achieve all the advantages of the pumps described above,including but not limited to the same compression ratios, operatingpressures, vibration reduction, and noise reduction of the smokeevacuation system 400.

FIG. 8 illustrates a cross-sectional view of a scroll compressor 800.The scroll compressor may include a stator scroll 484 and a movingscroll 486. The stator scroll 484 is fixed in position while the movingscroll 486 orbits eccentrically without rotating. The moving scroll 486may orbit eccentrically such that the moving scroll 486 does not rotateabout its own central longitudinal axis, but the central longitudinalaxis of the moving scroll 486 would orbit about a central longitudinalaxis of the stator scroll 484. The central longitudinal axes of thestator and moving scrolls 484, 486 extend perpendicular to the viewingplane of the scrolls 484, 486. The stator scroll 484 and the movingscroll 486 may be interleaved with each other to form discreet sealedcompression chambers 488.

A gas may enter the scroll compressor 483at an inlet 490. As the movingscroll 486 orbits, the inlet gas is first trapped in a compressionchamber 488. The compression chamber 488 moves a discreet volume of gasalong the spiral contour of the scrolls 484, 486 toward the center ofthe scroll compressor 483. The compression chamber 488, or sealed spacein which the gas resides, decreases in volume as the gas moves towardthe center of the stator scroll 484. This decrease in volume increasesthe pressure of the gas inside the compression chamber 488. The gasinside the sealed compression chamber 488 is trapped while the volumedecreases, thus pressurizing the gas. Once the pressurized gas reachesthe center of the scroll compressor 483 it is released through an outlet492.

Two or more scroll compressors may be disposed in series in order tocounterbalance vibrations that may be caused by the orbiting of themoving scroll 486. FIG. 9 illustrates a perspective view of two scrollcompressors 494, 496 disposed in series. Only the moving scrolls 498,500 are shown for illustrative purposes. The first moving scroll 498 maybe oriented at 180-degrees from the second moving scroll 500. The firstmoving scroll 498 of the first scroll pump 494 may orbit in an oppositedirection of the second moving scroll 500 of the second scroll pump 496.For example, the first moving scroll 498 may orbit counterclockwise andthe second moving scroll 500 may orbit clockwise. Other embodiments mayinclude first and second scroll pumps 494, 496 that are orientedopposite of the scrolls illustrated.

The two scroll pumps 494, 496 may be disposed in series within a sealedairflow path 408. In such a configuration, compressed gas exiting thefirst scroll pump 494at an outlet of the first scroll pump 494 may enteran inlet of the second scroll pump 496 to be further compressed. Asingle scroll pump, such as those described above, orbits eccentricallyand therefore inherently shifts its weight around while orbiting toproduce vibrations. The opposite orbiting movement of the two scrolls498, 500 in series, illustrated in FIG. 9 , may counterbalance oneanother in order to limit vibrations in the system 400.

Alternatively, another dual scroll pump embodiment may include twoscroll pumps 494, 496 aligned parallel to one another so that parallelflow paths pass through each scroll pump 494, 496. Each scroll pump 494,496 may have an inlet from a common airflow path 408 and an outletcommunicating with a common airflow path 408. Dual scroll pumps 494, 496aligned parallel in this manner may provide twice as much airflowthrough the system 400 than other embodiments described herein.

In one embodiment of the smoke evacuation system 400, the pump 410 maycomprise two scroll pumps of different sizes. FIG. 10A illustrates aperspective view of first and second scroll pumps 502, 504. For the sakeof simplicity in illustration, stator scrolls of the scroll pumps 502,504 are not shown. Rather, only the moving scrolls 502, 504 are shownfor illustrative purposes. The first scroll 502 may be a lowflow-capacity scroll that orbits at a relatively lowrevolutions-per-minute (“RPM”) compared to the other pumps describedherein. The second scroll 504 may be a high flow-capacity scroll thatalso orbits at a relatively low RPM. The high flow scroll 504 may have ahigher flow-capacity than the low flow-capacity scroll 502 even when thetwo are orbiting at the same RPM due to a larger diameter 506 comparedto a diameter of the low flow-capacity scroll 502.

The low-flow scroll 502 and the high flow scroll 504 may be disposed inseries, as described previously in reference to the dual in-line scrollpump illustrated in FIG. 9 . The two scrolls 502, 504 may also bedisposed next to each other as illustrated in FIG. 10A. Arrows 508 and510 indicate the orbiting direction of the low flow and high flowscrolls 502, 504, respectively. FIG. 10A illustrates both scrollsorbiting in a counter-clockwise direction. Other embodiments may includescrolls that orbit clockwise. Yet other embodiments may include scrollsthat orbit in opposite directions to one another.

Pairing a low flow scroll 502 with a high flow scroll 504 as describedabove has a number of advantages. The configuration illustrated in FIG.10A may allow for variable selectable flow rates without increasing theRPM of the scrolls. For example, as illustrated in FIG. 10B, the lowflow scroll 502 may produce a constant low-level airflow 512 over time.The high flow scroll 504 may provide higher flows over time. The highflow scroll 504 may be selectively turned on and off to provide discretehigher flows 514 when needed. Such a need may arise, for example, toovercome a temporarily increased pressure resistance (e.g., due toclogging) within the airflow path 408 of the smoke evacuation system400.

Thus, variable flow rates can be accomplished while maintaining a lowRPM of the orbiting scrolls. Maintaining low RPMs of the scrolls maydecrease vibrations and noise of the pump 410.

Vibration Absorption Mechanisms

Components of typical smoke evacuation systems, such as pumps andmotors, may create unwanted or even damaging vibrations. Vibrations candamage components of the system or shorten their useful lifespan.Vibrations can even cause components of the system to move across thesurfaces on which they rest, requiring that they be fixed to thesurface. This decreases the portability of the system and increases thedifficulty of installation. Vibration absorption mechanisms may beincorporated into the smoke evacuation system 400 to further limitvibrations. These absorption mechanisms can be used in conjunction withthe various pumps described herein, or they may be incorporatedseparately into various other embodiments of the system 400.

FIG. 11 illustrates in schematic form an embodiment of a smokeevacuation system 516 that includes an inner housing 518 and an outerhousing 520. The inner housing 518 may house the motor 412 and pump 410of the smoke evacuation system 516. In some embodiments, the innerhousing 518 may house various other components of the smoke evacuationsystem 516. For example, the inner housing 518 may house the motor 412,pump 410, and exhaust mechanism 414. Also, for example, the innerhousing 518 may only house the pump 410 or the motor 412. In theillustrated embodiment of FIG. 11 , the inner housing 518 also includesportions of the first zone 416 and second zone 418 of the airflow path408 (See FIG. 2 ).

The first zone 416 of the airflow path 408 may be an inlet to the pump410 that may pass through the inner housing 518. Likewise, the secondzone 418 of the airflow path 408 may be an outlet from the pump that maypass through the inner housing 518 as well. Other embodiments of a smokeevacuation system may include an inner housing 518 that houses all ornone of the first and second zones 416, 418 of the airflow path 408.

FIG. 11 illustrates a cross-sectional view of smoke evacuation system516 in order to show the configurations of the inner and outer housings518, 520. In some embodiments, the inner housing 518 may completelyencapsulate various components of the system 516, such as the pump 410and the motor 412, thus totally isolating them from other components ofthe system 516, such as the filter 406 and exhaust mechanism 414. Inother embodiments, the inner housing 518 may only partially surround orencapsulate these or other components.

The outer housing 520 may house other components of the smoke evacuationsystem 516 that are not housed within the inner housing 518. Forexample, the embodiment illustrated in FIG. 11 shows outer housing 520that houses the filter 406, exhaust mechanism 414, and portions of thefirst and second zones 416, 418 of the airflow path 408. The outerhousing 520 may also house the entire system, including the innerhousing 518 and components therein.

FIG. 11 illustrates a cross-sectional view of a smoke evacuation system516 in order to show the configurations of the inner and outer housings518, 520. In some embodiments, the outer housing 520 may completelyencapsulate various components of the system 516, such as the filter 406and the exhaust mechanism 414, thus totally isolating them from anexterior environment surrounding the system 516. The outer housing 520may also encapsulate the inner housing 518. The outer housing 520 maycompletely encapsulate components of the smoke evacuation system 516 notencapsulated by the inner housing 518, such as the filter 406 andexhaust mechanism 414. In other embodiments, the outer housing 520 mayonly partially surround or encapsulate these or other components.

Vibration absorption mechanisms may be disposed, and serve asinterfaces, between the inner and outer housings 518, 520. FIG. 12illustrates an inner housing 518 interfacing with an outer housing 520via various vibration absorption mechanisms 522. Only a portion of theouter housing 520 is shown for illustrative purposes. Various componentsof a smoke evacuation system 400 are also shown, including first andsecond zones 416, 418 of the airflow path 408, which may serve as aninlet and outlet of the pump disposed within inner housing 518. Thefilter 406 (illustrated in FIG. 11 ), motor 412, and first and secondzones 416, 418 of the airflow path 408 may be disposed within the outerhousing 520 but outside the inner housing 518. The pump 410 may beenclosed inside the inner housing 518 and therefore not shown in FIG. 12.

In the embodiment illustrated in FIG. 12 , vibration absorptionmechanisms 522 may comprise springs disposed between inner and outerhousings 518, 520. The pump and/or motor enclosed/housed within theinner housing 518 may create vibrations that result in unwanted movementor noise of the system. The vibration absorption mechanisms 522 mayabsorb these vibrations so that a substantial portion of the vibrationsare not transferred to the outer housing 520.

For example, the springs 522 illustrated in FIG. 12 may compress,stretch, or laterally flex due to vertical or horizontal vibrationalforces acting on the springs 522. These forces may be a result of theinner housing 518 vibrating up and down, or laterally. These movementscaused by the vibrating motor and/or pump within the inner housing 518may be transferred into the springs 522. As the springs 522 compress,stretch, or laterally flex, the spring may absorb a substantial portionof the vibrations. Thus, the vibrations may not be substantiallytransferred from the inner housing 518 to the outer housing 520.

FIG. 12 illustrates an embodiment wherein four vibration absorptionmechanisms 522 are disposed between the inner housing 518 and the outerhousing 520. Other embodiments may include more or less than fourvibration absorption mechanisms 522 disposed between the inner housing518 and the outer housing 520. The location of the vibration absorptionmechanisms 522 may also vary in other embodiments. For example, avibration absorption mechanism 522 may be disposed at the bottom centerof the inner housing 518, rather than just at the bottom four corners ofthe inner housing 518 as illustrated.

In the embodiment illustrated in FIG. 12 , a number of plates 524 may besecured to or integrally formed with the inner housing 518 and thevibration absorption mechanisms 522 may be secured directly orindirectly to the plates 524. Other embodiments may or may not includeplates 524. For example, other embodiments may have vibration absorptionmechanisms 522 that are secured directly to the inner housing 518. Otherembodiments may include more or less than two plates 524 secured to boththe inner housing 518 and vibration absorption mechanism 522 asillustrated in FIG. 12 .

FIG. 13A shows an inner housing 518 secured to an outer housing 520 viaplates 524 and vibration absorption mechanisms 526. The vibrationabsorption mechanisms 526 of the embodiment illustrated in FIG. 13A maybe ring isolators 526. Similar to the springs 522 disposed between theplates 524 and outer housing 520 illustrated in FIG. 12 , the ringisolators 526 may absorb vibrations from the pump 410 and/or motor 412housed within the inner housing 518 so that a substantial portion ofthose vibrations are not transferred to the outer housing 520.

FIG. 13B illustrates how the ring isolators 526 may be secured to thehousings 518, 520 and/or plates 524. The ring isolators 526 may beconfigured in a circular ring shape and be disposed between the plate524 and outer housing 520 so that the ring isolator 526 acts as abarrier between the two, as illustrated in FIGS. 13B and 13C. Two ormore securing mechanisms 528 may secure the plate 524 and outer housing520 to the ring isolator 526 on opposing sides of the ring isolator 526as shown. The securing mechanisms 528 illustrated in FIGS. 13B and 13Ccomprise a nut and bolt assembly. Other embodiments may include othersecuring mechanisms 528. For example, other embodiments may includesecuring mechanisms 528 that comprise nails, screws, adhesives, clips,hooks, and the like.

FIG. 13C illustrates how a ring isolator 526 may absorb vibrations. Thering isolator may be comprised of a flexible material such as anelastomer. For example, one embodiment of the ring isolator 526 may bemade of silicone. Other embodiments may include ring isolators 526 thatcomprise other elastomeric materials, such as rubber. The ring isolator526 may flex when acted upon by a force, such as the forces created byvibrations 530. FIG. 13C illustrates vibrations 530 pushing down on theplate 524. These vibrations 530 push down on the plate 524, which pushesdown on the ring isolator 526, which may cause the ring isolator 526 toflex in such a way so as to compress the ring isolator 526. Thecompressed ring isolator 526 may absorb the movement of the plate 524due to the vibrations 530 without transferring a substantial portion ofthat movement into the outer housing 520.

Vibrations 530 may be oscillatory movements that create forces that maypush downward, pull upward, or pull sideways on the plate 524. As willbe appreciated, the ring isolator 526 may absorb all of these potentialmovements of the plate 524 by deforming and/or flexing in all differentdirections. For example, the ring isolator 526 may expand and stretchtaller, or shift side to side in response to various vibrational forces.In this way, ring isolators 526 may absorb the vibrations 530 of theinner housing 518 so the vibrations 530 are not substantiallytransferred to the outer housing 520.

FIG. 14A illustrates an embodiment where the vibration absorptionmechanism comprises an elastomeric sheet 532. The elastomeric sheet 532may be disposed between the plates 524 and outer housing 520 similar tothe springs 522 and ring isolators 526 described herein. The elastomericsheet 532 may be a single sheet covering an entire area between thefirst housing 518 and the second housing 520 as shown in FIG. 14A. Otherembodiments may include multiple sheets 532. For example, in oneembodiment, the sheet 532 may comprise four separate sections disposedat the four bottom corners of the inner housing 518 and/or plates 524,similar to where the ring isolators 526 are disposed according theembodiment illustrated in FIG. 13A. Other embodiments may include twoseparate sheets 532, each connecting two corners of the inner housing518 and/or plates 524 to the outer housing 520.

FIG. 14B shows one way in which the elastomeric sheet 532 may be securedbetween the plate 524 and the outer housing 520. In the illustratedembodiment, two nuts molded into the sheet 532 provide a fixture throughwhich two screws/bolts may be threaded from above the plate 524 andbelow the outer housing 520. Other embodiments may include othersecuring mechanisms, such as nails, hooks, adhesives, and so forth. Oncesecured, the sheet 532 may absorb vibrations from the inner housing 518due to the pump 410 or motor 412 and substantially prevent thosevibrations from being transferred to the outer housing 520.

In addition to the various vibration absorption mechanisms describedherein, additional vibration absorption mechanisms may be employed inconjunction with those described in other embodiments. FIG. 15 shows atube configuration that may enhance the vibration absorptioncapabilities of various tubes. More specifically, FIG. 15 shows benttubes 536, 537 that may absorb vibrations due to their bentconfiguration. The tubes 536, 537 may be inlet and/or outlet tubes tothe pump 410 residing within the inner housing 518. The motor 412 may bedisposed outside the inner housing 518 and engage the pump 410 throughthe housing 518. The motor 412 and/or pump 412 may create vibrations inthe system that may travel into the inner housing 518 and through thetubes 536, 537.

The tubes 536, 537 may include a U-shaped portion 538 at one or morelocations along the length of the tubes 536, 537. The U-shaped portions538 of the tubes 536, 537 may allow the tubes 536, 537 to flex inresponse to vibrations to a greater degree than straight tubes having noU-shaped portions 538. The U-shaped portions 538 of the tubes 537 alsomay increase the total length of the tubes 536, 537 to increase theamount of tube material available to absorb and dampen vibrations. Inthe embodiment shown in FIG. 15 , each tube 536, 537 has one U-shapedportion 538. Other embodiments may include more than one U-shapedportion 538. Some embodiments may include tubes 536, 537 bent into othershapes, such as S-shaped portions or the like.

The U-shaped portions 538 of the tubes 536, 537 may be made of materialthat is the same or similar to the rest of the tubes 536, 537. Someembodiments may include U-shaped portions 538 that are made of adifferent material than the rest of the tubes 536, 537. For example,some embodiments may include U-shaped portions 538 that are made of anelastomeric material. A U-shaped portion 538 made of an elastomericmaterial, for example rubber, may absorb vibrations to a greater degreethan more rigid materials such as plastics and the like.

Three different configurations of tubes 540 configured to absorbvibrations are illustrated in FIGS. 16A through 16C. FIG. 16Aillustrates a tube 540 having a flexible portion 542. The flexibleportion 542 may be made of an elastomeric material such as silicone,rubber, or the like. FIG. 16B illustrates a tube 540 that includes aU-shaped portion 544 similar to those U-shaped portions 538 illustratedin FIG. 15 . The U-shaped portion 544 may be made of material similar tothe rest of the tube 540 or it may be made of elastomeric material suchas silicone, rubber, or the like. FIG. 16C illustrates a tube 540 thatincludes 90-degree bent portions 546, in order to accomplish the samevibration absorption capacity of the tubes 540 described above. Again,the bent portions 546 may be made of material similar to the rest of thetube 540 or may be made of elastomeric material such as silicone,rubber, or the like.

In addition to the absorption mechanisms described above, which may bedisposed between the inner housing 518 and outer housing 520, additionalabsorption mechanisms may be disposed on an outside surface of the outerhousing 520. The smoke evacuation system 400 may be placed on a supportsurface, such as a table or countertop when in use. Vibration of theouter housing, due to the operation of internal components of the system400 such as the motor 412 and/or pump 410, may cause the entire system400 to bounce/travel along the support surface.

Additional vibration absorption mechanisms may be disposed on a bottomoutside surface of the outer housing 520 to act as an interface betweenthe smoke evacuation system 400 and the support surface on which theouter housing 520 is placed in order to reduce this effect. Thevibration absorption mechanisms may act to absorb the vibrations so thevibrations are not substantially transferred to the support surface. Thevibrations absorption mechanisms may also provide greater frictionbetween the outer housing 520 and a support surface to reduce travelalong the surface due to vibrations.

FIG. 17A shows an outer housing 520 that includes a number of feet 548.These feet 548 are vibration absorption mechanisms. The feet 548 aredisposed on a bottom surface 550 of the outer housing 520 and may act asan interface between the outer housing 520 and a support surface onwhich the outer housing 520 is placed. The embodiment illustrated inFIG. 17A includes four feet 548 disposed on the bottom surface 550.Other embodiments may include more or less than four feet 548 that maybe arranged in any number of configurations. For example, one embodimentmay include only three feet 548. Other embodiments may include five ormore feet 548 with some of the feet 548 disposed near the center of thebottom surface 550 as well as the corners.

FIG. 17B illustrates a cross-sectional view of one of the feet 548illustrated in FIG. 17A. The foot 548 may be comprised of a flexiblematrix 554 secured to the bottom surface 550 via a rigid or semi-rigidbolt 552. The bolt 552 may be threaded or otherwise secured to thebottom surface 550. The bolt 552 may protrude beyond the bottom surface550 and the flexible matrix 554 may be molded around the protrusion ofthe bolt 552.

The flexible matrix 554 of the foot 548 may have a first diameter D₁ anda second diameter D₂. The first diameter D₁ and the second diameter D₂may vary in size. The first diameter D₁ may be smaller than the seconddiameter D₂. A contact pressure between the foot 548 and a supportsurface may increase as the diameter of the foot 548 decreases. Also,certain diameters may absorb a given range of vibrational frequenciesbetter than others. It may therefore be advantageous to vary thediameter of the foot 548 as shown in FIG. 17B.

For example, D₁ may absorb a first frequency of vibrations, or firstrange of frequencies, and D₂ may absorb a second frequency ofvibrations, or second range of frequencies. Therefore, having a foot548, such as the foot 548 illustrated in FIG. 17C, with variousdiameters D₁. D₂ may enable the foot 548 to substantially absorb boththe first and second frequencies, or ranges thereof. One will appreciatethat other embodiments may include feet with any number and combinationof different diameters to meet the specific range of frequencies beingabsorbed.

FIG. 17C shows another embodiment of a foot 548 that includes a firstdiameter D₁ that is smaller than a second diameter D₂. In thisembodiment, the edge profile 556 of the foot 548 is straight so that thefoot 548 substantially resembled an inverse cone. Other embodiments mayinclude edge profiles 556 that result in various other shapes.

It will be appreciated that the feet 548 may be secured to the bottomsurface 550 in a variety of ways. For example, in one embodiment, thefeet 548 may be secured via hooks, nails, adhesives, or the like,without the need for a bolt 552 as shown in FIG. 17B. The feet 548,including other embodiments of feet described herein, may be made of anelastomeric material, such as rubber, silicone, or the like. Theelastomeric material of the flexible matrix 554 may absorb vibrationsfrom the outer housing 520 and provide added friction between the bottomsurface 550 of the outer housing 520 and a support surface on which theouter housing 520 is placed.

FIG. 18A illustrates a number of feet 558 disposed on the bottom surface560 of an outer housing 520. In this embodiment, nine feet 558 serve asan interface between the bottom surface 560 and a support surface.Increasing the number of feet 558 may increase the vibration absorptioncapacity of the system. It may also increase the friction between thebottom surface 560 of the outer housing 520 and a support surface tominimize vibrational travel. Other embodiments may include more thannine feet 558 disposed on the bottom surface 560 in order to increasefriction and vibration absorption capacity.

FIG. 18B illustrates a cross-sectional view of two of the feet 558 shownin FIG. 18A. There may be slight variations in the bottom surface 560 ofthe outer housing 520 and/or the support surface 564 that cause thesurfaces 560, 564 to be uneven. This may result in inconsistent contactbetween some of the feet 558 and the support surface 564. Flexiblespacers 562 may be disposed on the feet 558 to compensate for unevensurfaces 560, 564 so that all the feet 558 may be in contact with thesupport surface 564 despite unevenness.

As shown in FIG. 18B, the spacers 562 may compress from a firstthickness X₁ to a second thickness X₂. The spacers 562 may be made of anelastomeric material, such as silicone or rubber, so that the thicknessX of the spacer 562 may vary depending on the unevenness of the supportsurface 564 on which the outer housing 520 is placed. In this way, allof the feet 558 may be in contact with the support surface 564 in orderto increase vibration absorption capability and friction between thebottom surface 560 and the support surface 564. The spacers 562 may alsoprevent the outer housing 520 from rocking due to a space or gap betweenthe feet and the support surface.

FIG. 19A shows a cross-sectional view of one embodiment of a foot 566for absorbing vibrations. This embodiment is similar to the embodimentillustrated in FIG. 17C, except here the first diameter D₁ is greaterthan the second diameter D₂. FIG. 19B illustrates how the foot 566,which may be comprised of an elastomeric material, may deform due tovibrations in the outer housing 520. As shown, vibrational movements ofthe outer housing 520, illustrated by arrows 576, are transferred to thefoot 566. The foot 566 may laterally deform, as illustrated by arrows578, from a first shape 572 to a second shape 568. This lateraldeformation and/or change in shape of the foot 566 may occur while theinterface 574 between the foot 566 and the support surface remainssubstantially constant. In this way, the foot 566 may absorb vibrationswithout substantially transferring them to the support surface 570 ortraveling across the support surface 570.

The various embodiments of vibration absorption mechanisms describedherein, including vibration absorption mechanisms disposed between innerand outer housings, flexible tubing, U-shaped tubing, and feet disposedon a bottom surface of the outer housing, may be employed singly ortogether in a multitude of combinations. These embodiments may also beincluded within various embodiments of a smoke evacuation system thatincludes various types of pumps, blowers, and/or compressors. Thevibration absorption mechanisms described herein, combined with pumpsthat reduce vibrations and noise, may provide a substantial decrease invibrations and noise inherent in typical smoke evacuation systems.

Motors and Methods of Control

The smoke evacuation system 400 illustrated in FIG. 2 includes motor 412engaging the pump 410. The motor may rotate a rotary shaft of thevarious pumps 410 described herein. In one embodiment, the motor 412 maybe a permanent magnet synchronous motor. Other embodiments may include abrushless DC motor. Brushless motors may have large starting torquesfrom a fully stopped condition for use with the various pumps describedherein. Brushless motors may also have less noise, greater dynamicresponse, and better speed-vs.-torque characteristics than brushedmotors.

The pump 410 may create a pressure differential between a gas enteringthe pump 410 and a gas exiting the pump 410, as described above. Thispressure differential, or compression ratio of the pump 410 may resultin a high starting torque of the motor 412 in order to initiate themotor 412 rotating the pump 410.

Motor control methods may be employed to reduce the vibrations andincrease motor efficiency and lifespan. Unwanted debris from the outsideenvironment may inadvertently enter the airflow path 408 and causeclogging and/or blockages. These blockages within the system can causepump and airflow path resistance pressures to rise as airflow isimpeded. In order to maintain necessary airflow while blockages arepresent, pumps and/or motors may need more power and/or speed in orderto compensate. Increased speed and/or power may diminish the efficiencyof the motor and pump as well as decrease their lifespan. Variouscontrol methods of a smoke evacuation system, particularly methods ofmotor regulation, as described herein, may maintain airflow rates,increase motor efficiency, and preserve the lifespan of the motor and/orpump, especially when blockages and/or clogging of the system occurs.

A method 580 for regulating the motor to reduce noise and vibration in asmoke evacuation system is shown in FIG. 20 . In a first step 586, thesystem may sense or detect whether smoke is present to be evacuated ornot. This detection may be done automatically when the practitionerbegins cutting a patient during electrosurgery, or a separate smokesensor may be employed to detect smoke present at cutting site. If smokeis present to be evacuated, then a next step 582 of the method may be toregulate the motor so that the rotational speed of the motor results infull smoke evacuation. If no smoke is present to be evacuated, then thenext step may be to regulate the motor to operate at a rotational speedso that the motor is in sleep mode 584.

In one embodiment, a method of regulating the motor may include varyinga supply of electrical current to the motor. For instance, the method580 may include supplying a first amount of current to the motor tocause the motor to operate at a first performance level. Alternatively,a second amount of current may be supplied to the motor to cause themotor to operate at a second performance level. The supply of currentmay be accomplished by varying a pulse width modulation (PWM) duty cycleof an electrical input to the motor. In other embodiments, the currentmay be varied by adjusting the frequency of the current supplied to themotor. The motor may be engaged with a rotary mechanism, such as thecompressors and blowers described above, so that reducing the duty cycleor frequency of a current input to the motor decreases the rotationalspeed of the rotary mechanism.

In one embodiment, a regulation of the motor may depend on an initialcondition, such as the rotational speed of the rotary mechanism. Forexample, once the system is running, the regulation of the motor mayoperate the motor at a constant speed that equals the initial rotationalspeed of the motor. In one embodiment, the first performance level ofthe motor may result in a first rotational speed of a rotary shaft ofthe motor engaging a rotary mechanism. The first performance leveltherefore, may result in a faster rotation of the rotary mechanism. Thisfirst performance level, and corresponding rotation speed of the rotarymechanism, may be the speed needed for normal suction of a gas throughthe airflow path. A second performance level may be slower than thefirst so that the second performance level causes the rotary mechanismto operate at a speed lower than the first level.

The first performance level may be employed when there is no smokeproduced by the electrosurgical instrument, but it is advantageous tokeep the smoke evacuation system active. For example, a practitionerperforming electro-surgery may temporarily have no need to suck smokeinto the system to be filtered because the practitioner is not currentlycutting the flesh of the patient and producing smoke. Instead ofcompletely turning off the smoke evacuation system every time smoke isnot being produced, and suction is temporarily not needed, the motor mayswitch to the second, slower performance level.

When the practitioner begins cutting again with the electrosurgicalinstrument, producing unwanted smoke, the motor may be switched back tothe first, higher performance level, thus creating a higher vacuumpressure necessary to suck smoke into the system to be filtered. Thislower second performance level may be thought of as a sleep mode. Insleep mode, the motor may still run, but not to its full or usualstrength/rotational speed. The sleep mode may preserve the lifespan ofthe motor, and/or rotary mechanism with which it is engaged, by reducingthe stress and wear caused by running the motor at full capacity at alltimes.

The second, lower performance level of the motor may be moreadvantageous than turning the motor completely off when suction is notneeded, and switching the motor on when suction is needed. This isbecause a practitioner may need to use the suction only intermittentlyduring long periods of surgery. Turning a motor on from a completelyturned-off state requires high start-up torques in order to overcome thestandstill inertia of the motor. Repeatedly turning the motor on from acompletely off mode in this manner is inefficient and may decrease thelifespan of the motor. Alternatively, employing a sleep mode asdescribed above, with a first and second performance level, allows themotor to remain on during intermittent non-use of the system duringsurgery, so that activation of the first performance level when suctionis needed can be done without the higher torques needed to overcomestandstill inertia.

In one embodiment, a method of motor control may be employed to limitsubstantial overheating of the motor. The motor may overheat if ablockage in the airflow path of the smoke evacuation system causes anoverworking of the motor and/or rotary mechanism as they attempt tocompensate for the blockage and maintain a constant airflow rate.Therefore, in the method 580 for regulating the motor, a further stepmay include detecting an operational parameter. The operationalparameter may be, but is not limited to, the temperature of the motorand/or rotary mechanism and/or the pressure in the airflow path of thesmoke evacuation system.

In one embodiment, the next step 590 may be to compare the detectedoperational parameter to an operational parameter limit. This parameterlimit may be preset. If the detected operational parameter is greaterthan or equal to the operational parameter limit, the next step 592 ofthe method may include altering the operational parameter to be lessthan the operational parameter limit. In one embodiment, the method mayinclude setting a temperature limit and sensing a temperature of themotor and/or rotary mechanism. When the temperature of the motor and/orthe rotary mechanism is equal to or greater than the temperature limit,the motor may be shut off or its performance level reduced.

In one embodiment, the method may include defining a pressure limit andsensing a pressure within the circulation path of the rotary mechanismand/or the airflow path of the smoke evacuation system. A pressureinside the airflow path or rotary mechanism may increase when blockageoccurs inside the airflow path as described above. In order to preventthe motor from overextending itself to overcome these higher pressures,the motor may be shut off or its performance level reduced, as describedabove, when the sensed pressure is equal to or greater than the setpressure limit. In one embodiment, the method may include disengagingthe motor from the rotary mechanism. The motor may disengage from therotary mechanism via a clutch.

In one embodiment, the method may include manipulating one or moreorifices disposed near the motor within the airflow path of the smokeevacuation system. This method may also include defining a pressurelimit and sensing a pressure within the airflow path as described above.When the sensed pressure is equal to or greater than the pressure limit,the one or more orifices may be opened to allow air to flow from insidethe otherwise closed airflow path of the system to the surroundingenvironment, or vice versa. Opening the one or more orifices may reducethe pressure within the system, thus preventing the motor and/or rotarymechanism from attempting to compensate for the higher pressure.

The various methods of regulating the motor and or smoke evacuationsystem described herein may be employed in conjunction with any of theembodiments of a smoke evacuation system described above. These methodsmay also be employed independent of the various other embodiments.

The present invention may be embodied in other specific forms withoutdeparting from its spirit or essential characteristics. The describedembodiments are to be considered in all respects only as illustrativeand not restrictive. The scope of the invention is therefore indicatedby the appended claims rather than by the foregoing description. Allchanges that come within the meaning and range of equivalency of theclaims are to be embraced within their scope.

What is claimed is:
 1. A smoke evacuation assembly, comprising: afilter; a pump comprising a sealed positive displacement airflow path;and a motor engaging the pump; wherein the pump has a first operatingpressure and a second operating pressure, and wherein a first flow rateof a gas flowing through the path at the first operating pressure issubstantially similar to a second flow rate of a gas flowing through thepath at the second operating pressure.
 2. The smoke evacuation assemblyof claim 1, wherein a difference in pressure between the first operatingpressure and the second operating pressure is equal to or greater than1.5 psig.
 3. The smoke evacuation assembly of claim 2, wherein the pumpis a hybrid regenerative blower with impeller features that createcompression of a gas passing through the airflow path.
 4. The smokeevacuation assembly of claim 1, further comprising a pump with first andsecond rotary elements disposed within a single circulation path,wherein: the first rotary element and the second rotary element are inmating cooperation and configured to produce a gas flow through thecirculation path; the first rotary element is in series with the secondrotary element; the first rotary element and the second rotary elementare each secured to and driven by cooperative counter-rotating driveshafts; or the pump comprises a two stage dual rotary vacuum pump, thefirst rotary element being the first stage and the second rotary elementbeing the second stage.
 5. The smoke evacuation assembly of claim 1,further comprising: a first housing at least partially surrounding thesmoke evacuation assembly; a second housing at least partiallysurrounding the motor and the pump; an interface between the firsthousing and the second housing comprising one or more vibrationabsorption mechanisms; and one or more vibration absorption mechanismsdisposed on a bottom outer surface of the first housing.
 6. The smokeevacuation assembly of claim 1, wherein the pump comprises a scrollpump.
 7. The smoke evacuation assembly of claim 1, wherein the airflowpath comprises one or more at least partially flexible tubes, wherein atleast one or more of the one or more at least partially flexible tubesis disposed between the filter and the pump.
 8. The smoke evacuationassembly of claim 7, further comprising an exhaust mechanism, wherein atleast one of the at least partially flexible tubes is disposed betweenthe pump and the exhaust mechanism.
 9. A smoke evacuation system,comprising: an airflow path comprising: a first zone maintained at firstpressure; and a second zone maintained at a second pressure; a pumpconfigured to draw a gas from the first zone to the second zone; and amotor engaged with the pump; wherein a pressure ratio of the secondpressure to the first pressure is equal to or greater than
 2. 10. Thesmoke evacuation system of claim 9, wherein the pump is a compressor.11. The smoke evacuation system of claim 10, wherein the compressor is alobe compressor.
 12. The smoke evacuation system of claim 10, whereinthe compressor is a scroll compressor, the scroll compressor comprisinga first scroll and a second scroll, the first scroll being a statorscroll and the second scroll being a moving scroll.
 13. The smokeevacuation system of claim 12, wherein the scroll compressor is a dualin-line scroll compressor comprising: first and second stator scrolls;and first and second moving scrolls; wherein the first stator scroll andfirst moving scroll are disposed together and the second stator scrolland second moving scroll are disposed together; wherein the first statorscroll is in-line with the second stator scroll; and wherein the firstmoving scroll in a first direction and the second moving scroll rotatesin a second direction that is opposite of the first direction.
 14. Amethod of reducing vibration and noise in a smoke evacuation assemblycomprising: regulating a motor engaged with a rotary mechanism, therotary mechanism disposed within a circulation path of the smokeevacuation assembly, wherein regulation of the motor comprises varying asupply of current to the motor in order to operate the motor at a firstrotational speed and a second rotational speed; and wherein the firstrotational speed is greater than the second rotational speed such thatthe motor operates at a first performance level at the first rotationalspeed and a second performance level at the second rotational speed, thesecond performance level being a sleep mode.
 15. The method of claim 14,wherein varying the supply of current is accomplished by varying PWMinputs of current through the motor.
 16. The method of claim 14, whereinvarying the supply of current is accomplished by adjusting a frequencyof the current.
 17. The method of claim 14, wherein the motor regulationdepends on an initial condition, the initial condition being therotational speed of the rotary mechanism engaged by the motor.
 18. Themethod of claim 14, the regulation of the motor comprising: supplyingcurrent to the motor through PWM, the PWM having a duty cycle; defininga temperature limit; periodically sensing a motor temperature; reducingthe duty cycle when the motor temperature is equal to or greater thanthe temperature limit.
 19. The method of claim 14, the regulation of themotor comprising: defining a pressure limit; periodically sensing anairflow path pressure; disengaging the motor from the rotary mechanismby means of a clutch when the pressure level is equal to or greater thanthe pressure limit.
 20. The method of claim 14, further comprising:defining a pressure limit; sensing an airflow path pressure; opening anorifice when the circulation path pressure is equal to or greater thanthe pressure limit; and closing the orifice when the airflow pathpressure is less than the pressure limit; wherein the orifice isdisposed in the airflow path local to the motor on one or bother sidesof the motor so that opening the orifice minimizes a pressure ratio tothat of the pump without any line head pressures.